Transfer and ejection mechanism for forging machine

ABSTRACT

A transfer and ejection mechanism for a forging machine is disclosed. The transfer operates through a closed path including a first portion of arcuate movement in a direction substantially perpendicular to the die face, a second portion of transfer movement in a substantially straight line to a position adjacent to a subsequent die, and a third portion of arcuate movement inwardly toward the die face and substantially perpendicular thereto. The in and out movement eliminates the need for a precise adjustment of the knockout and rearward positioning of subsequent dies with respect to the preceding dies. The final movement back to the initial position is along a curved path wherein the transfer fingers are raised clear of the tool and return movement is commenced before the tool withdraws from the die. This substantially reduces the dwell required at the delivery position. The ejection mechanism causes rapid ejection to a blank-gripping position, slower ejection during gripping, and subsequent fast ejection to complete the blank ejection. This is particularly important when transferring blanks with short shanks since it provides sufficient time to grip a blank without increasing ejection time.

i [72] Inventors United States Patent Gene E. Allebach; Richard Edmondson, both of Tiffin, Ohio [21 App]. No. 784,806

[22] Filed Dec. 18,1968

[45] Patented Sept. 14, 1971 [73] Assignee The National Machinery Company Tiffin, Ohio [54] TRANSFER AND EJECTION MECHANISM FOR [56] References Cited UNITED STATES PATENTS 3,120,770 2/1964 Hoyt 72/422 3,154,801 11/1964 Byarn... l0/l2T 3,263,480 8/1966 Carlson l0/l2.5 X 3,389,594 6/1968 Seppi 10/12 TX Primary Examiner-Charles W. Lanham Assistant Examiner-R. M. Rogers Attorney-McNenny, Farrington, Pearne and Gordon ABSTRACT: A transfer and ejection mechanism for a forging machine is disclosed. The transfer operates through a closed path including a first portion of arcuate movement in a direction substantially perpendicular to the die face, a second portion of transfer movement in a substantially straight line in a position adjacent to a subsequent die, and a third portion of arcuate movement inwardly toward the die face and substantially perpendicular thereto. The in and out movement eliminates the need for a precise adjustment of the knockout and rearward positioning of subsequent dies with respect to the preceding dies. The final movement back to the initial position is along a curved path wherein the transfer fingers are raised clear of the tool and return movement is commenced before the tool withdraws from the die. This substantially reduces the dwell required at the delivery position. The ejection mechanism causes rapid ejection to a blank-gripping position, slower ejection during gripping, and subsequent fast ejection to complete the blank ejection. This is particularly important when transferring blanks with short shanks since it provides sufficient time to grip a blank without increasing ejection time.

PATENTEB SEPMISTI SHEEI 1 OF 5 TRANSFER AND EJECTION MECHANISM FOR FORGING MACHINE BACKGROUND OF INVENTION This invention relates generally to automatic forging machines and more particularly to novel and improved highspeed knockout and transfer means for such machines.

PRIOR ART Automatic forging machines often include a progressive header in which blanks are progressively transferred to a series of die stationsat which they are progressively formed to a desired shape. Such machines normally provide automatic knockout means which eject a blank from a die station and a transfer mechanism which transfers the ejected blank to a subsequent die station. Examples of such machines are illustrated in the U.S. Letters Pats. to Friedman Nos. 2,542,864, 2,599,053, 2,687,660, and 2,721,343.

Generally the transfer mechanism of such machine must dwell in its delivery position until the slide carries the too] clear of the transfer fingers and must also dwell in the pickup position while the blank is ejected from the die. Further, in such machines the rate of ejection of the blank from the die must be limited to a rate which permits proper gripping of the blank in a reliable manner.

Since such transfer mechanisms have been required to dwell during substantial portions of the overall machine cycle, the transfer mechanism has operated with an active cycle time which is substantially shorter than the overall cycle time of the machine. In many instances this has resulted in a limitation on the operational speed of the machine since higher machine speeds have not provided sufficient time for proper ejection and transfer of the blank.

Further the transfers of such machines normally do not provide any in and out movement of the blank as it is transferred from one die station to the next. It has, therefore, been necessary in many instances to accurately adjust the knockout pin so that it is exactly flush with the face of the die at the completion of the knockout operation and/or to position subsequent dies back from the plane of the face of the preceding die. Such arrangements have been required to insure that the blank will be completely clear of the die at the completion of the ejection and will not catch during transfer on the subsequent die or the knockout pin of the subsequent die station.

SUMMARY OF INVENTION There are several aspects to this invention. First a machine incorporating the present invention includes a transfer mechanism arranged so that the dwell periods at the delivery station are substantially shortened. Consequently the active cycle time of the transfer closely approaches the complete cycle time of the overall machine. With this arrangement the machine can be operated at higher operating speeds without materially reducing the active cycle time of the transfer and without encountering limiting operating speeds in the transfer. Further in accordance with another aspect of this invention, the knockout mechanism is arranged to reliably operate at high speeds even when transferring blanks with short shanks. Still further in accordance with another aspect of this invention, the transfer is provided with an in and out movement so that .a blank carried by the transfer is moved out clear of the die from which it is ejected and is moved back in toward the subsequent die after it is positioned in alignment with the subsequent die. This eliminates the problem of exact adjustment of the knockout .pin and eliminates the need to stagger subsequent dies back from the plane of the face of the preceding die.

In the illustrated embodiment of this invention a progressive forgingsmachine is provided with a transfer mechanism wherein the fingers, after gripping a blank, move out from the die along an arcuate path, then move with straight line motion to a position substantially aligned with the subsequent die. then move inwardly along an arcuate path to complete the positioning of the blank at the subsequent die. It is at this point in the operation that the tool associated with the subsequent die station pushes the blank out of the gripping fingers into the subsequent die. As soon as the blank is released and before the tool withdraws from the subsequent die the transfer commences the return movement toward the first die. Such return movement occurs along an arcuate path in which the fingers are opened and lifted to clear the tool and the operating cycle of the transfer approaches the full-operating cycle of the machine.

In the illustrated embodiment a knockout mechanism is provided wherein the knockout operates at a high velocity to eject the blank to a position in which the transfer fingers can move in to grip the blank. After the initial portion of an ejection at a high rate of speed, the rate of ejection is slowed to allow the gripping fingers of the transfer to close on, and grip, the blank. After gripping is established, the rate of ejection is again accelerated to minimize the time required for the remaining portion of the ejection.- With this arrangement wherein the ejection is rapid initially, is slowed for actual gripping, and is subsequently rapid to complete the ejection, a high-speed operation can be obtained even when transferring blanks with shanks. This ejection mechanism cooperates with the improved transfer mechanism to further increase the practical operating rate of the ejection and transfer system and permits higher machine speeds without sacrificing reliability of operation.

DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevation of a combined machine adapted to form threaded articles such as bolts, screws, and the like incorporating a transfer mechanism and a knockout mechanism in accordance with a preferred embodiment of this invention;

FIG. 2 is a schematic perspective view of the transfer mechanism with parts broken away for purposes of clarity;

FIG. 3 is an enlarged plan view of the transfer mechanism with the gripper fingers removed;

FIG. 4 is a fragmentary cross section taken generally along 4-4 of FIG. 3;

FIG. 5 is a fragmentary cross section taken generally along 5--5 of FIG. 3;

FIG. 6 is a schematic perspective view illustrating the drive mechanisms of the transfer; and,

FIG. 7 is an enlarged fragmentary side elevation, partially in section, illustrating the knockout drive mechanism.

Referring to FIG. 1, the illustrated machine is particularly adapted to form bolts, screws, and the like from rod or wire stock. The machine includes a frame 10 having a crankshaft ll journaled thereon. A header slide (not illustrated) is reciprocated toward and away from a die breast (also not illustrated) by a pitman connecting the slide to the crankshaft 11. The crankshaft l l is driven by a motor 12 which is connected by belts 13 to a fly wheel 14 mounted on the end of the crank shaft 11. A transfer mechanism, indicated generally at 16, is powered by an upwardly extending drive shaft 17 which is connected by bevel gears 18 to an accessory drive shaft 19. The accessory drive shaft 19 is driven through gearing (not illustrated) from the crankshaft 11 at the same speed as the crankshaft. The upper end of the drive shaft 17 is connected to the camshaft 21 of the transfer mechanism 16 and provides the principal motive power for the transfer mechanism.

The machine illustrated also includes a knockout mechanism illustrated generally at 22. The knockout mechanism includes an oscillating camshaft 23 driven by a pitman 24 connected to an eccentric portion 26 on the crankshaft 11. The machine is also provided with a stock feed mechanism indicated at 27 and a pointer indicated at 28.

Reference may be made to the copending application Ser/ No. 780,153, filed Nov. 29, 1968 for a more detailed description of the basic machine. Reference may also be made to the copending application Ser. No. 781,092, filed Dec. 4, 1968 for a more detailed description of the pointer 28.

Referring to FIGS. 2 through 6, the transfer mechanism includes a transfer frame 31 which is secured to the machine frame 10. The camshaft 21 is journaled in spaced bearings on the transfer frame 31 so its axis of rotation is fixed with respect to the frames and 31.

A first transfer support housing 32 is supported on the transfer frame 31 by a pivot connection 33 so that it may be pivoted around a pivot axis 34 from a normal or lowered position illustrated in FIGS. 4 and 5 to a raised position. The support housing 32 rotates to a raised position to provide for raising of the transfer fingers to clear the tool. This is described in more detail below.

A second transfer support housing 36 is pivotally connected to the first transfer support housing 32 by a pivot 37. Pivotal movement of the second transfer support housing 36 from the illustrated position in FIGS. 4 and 5 in an anticlockwise direction is provided to produce arcuate movement of the transfer fingers substantially perpendicular to the face of the dies. This movement, which is discussed in more detail below, is provided to move a blank away from the face of one die at the beginning of a transfer operation and to provide return of the blank toward the face of a subsequent die at the completion of the transfer operation.

Mounted on the second transfer support housing 36 is a transfer bar which is supported thereon for longitudinal reciprocation. This longitudinal movement of the transfer bar 38 provides the principal movement of the transfer fingers 39 (illustrated in FIG. 6) from the gripping position to the delivery position. In FIGS. 2 through 5 the transfer fingers are not illustrated for purposes of simplification but it should be understood that in a progressive forming machine having a plurality of die stations, a sufficient number of pairs of transfer fingers are provided, on the transfer bar 38, to progressively transfer the blanks to each of the die stations.

There are four separate power drive mechanisms for operating the transfer. A first power drive mechanism operates to cause raising pivotal movement of the first transfer housing 32 about the pivot axis 34. The second power drive mechanism causes pivotal movement of the second transfer housing 36 with respect to the first transfer support housing 32 about the pivot 37. The third power drive mechanism operates to open and close the fingers 39, and the fourth power drive mechanism operates to longitudinally reciprocate the transfer bar 38. All of the power drive mechanisms with the exception of the fourth power drive mechanism for reciprocating the transfer bar are powered by the camshaft 21.

The mechanism for pivoting a first transfer housing 32 about the pivot axis 34 includes a cam 41 mounted on the camshaft 21. A roller cam follower 42 is journaled on a rocker arm 43 and is positioned for engagement with the cam 41. The rocker arm 43 is mounted on a pivot shaft 44 journaled on the frame 31 for pivotal movement about a pivot axis 46. A lever 47 is pivoted at 48 to the rocker arm 43 and is positioned with respect to the rocker arm 43 by a bolt 49. The bolt 49 is sized to break in the event an overload is encountered. During normal operation, the lever 47 is fixed with respect to the rocker arm '43 so the rocker arm 43 and lever 47 may be considered as a single element from an operational standpoint. Mounted on the end of the lever 47 is a bearing pad 51 positioned to engage a pair of rollers 52 which are journaled on the first support housing 32.

The cam 41 and its associated linkage is proportioned so that when the elements are in the lowered position, illustrated in FIG. 5, the cam follower 42 engages a low portion of the cam 41 and the first support housing 32 is in its normal position. When a lift portion of the cam 41 passes the follower 42, the rocker arm 43 rotates in an anticlockwise direction and, through the engagement of the bearing pad 51 with the followers 52, causes anticlockwise rotation of the first support housing 32 around its pivot axis 34. This operates to lift the forward end of the transfer mechanism. After the lift portion of the cam 41 passes the follower .42, the first support housing 32 drops back to the illustrated position.

A holddown mechanism is provided to resiliently urge the support housing 32 toward the position illustrated. This holddown mechanism, which is best illustrated in FIG. 4, includes a support member 50 pivoted on the frame 31 by the pivot 33. the same pivot which connects the support housing 32 to the frame 31.

During normal operation the support member 50 is locked in the position illustrated in FIG. 4. This locking is provided by a pair of clamped elements 55 which press a cross pin 53 carried by the support member 50 into tight engagement with associated stop surfaces 54 formed on the frame 31. A stud and nut assembly 56, associated with each clamp element 55, serves to releasably hold the associated clamp element in the locked position. The first support housing 32 is formed with a cutout 57 so that the frame 31 can be formed with the projection providing the surface 54 proportioned to extend up through the housing 32.

Mounted on the end of the support member 50 is a spring assembly 58 provided with a compression spring 59 which urges a plunger 61 in a downward direction into engagement with a roller 62 journaled on the first support housing 32. The spring 59 functions to resiliently urge the first support housing 32 in a clockwise direction toward the normal position illustrated and permits anticlockwise movement from this position under the influence of the cam 41 and its driven linkage. This mechanism, however, can be easily released to permit the entire transfer mechanism to be pivoted up to an accessible position for adjustment and service. When adjustment or service is required, the nuts 56 are loosened to release the clamping of the clamp elements 55. The elements 55 can then be pushed forward clear of the lockpin 53. This permits the support member 50 to be pivoted in anticlockwise direction and frees the first support housing 32 for similar pivotal movement to raise the entire transfer mechanism up for servicing. During such movement the follower arm 43 which is pivoted on the frame 31 remains in the illustrated position.

The pivotal movement of the second support frame 36 about its pivot 37 is provided by a second drive mechanism best illustrated in FIGS. 4 through 6. This mechanism includes a cam 66 mounted on the camshaft 21 for engagement by a roller follower 67 journaled on a rocker arm 68. The rocker arm 68 is clamped to one end ofa pivot-shaft 69 which is journaled on the frame 31 for pivotal movement about its axis. The pivot shaft 69 is provided with a projection 71 engageable with the rearward end of the pin 72 which is in turn slidably supported on the first support frame 32. The forward end of the pin 72 engages the rearward side of the second support housing 36 and operates when it is pushed forwardly by the projection 71 to cause anticlockwise rotation of the second support housing 36. The cam 66 and the linkage driven thereby is proportioned so that rotation of a lift portion of the cam 66 past the follower roller 67 causes anticlockwise rotation of the rocker arm 68. This causes the pin 72 to be pushed forward to produce anticlockwise rotation of the second support housing 36. A compression spring 73 is connected between the first housing support 32 and the second housing support 36 to resiliently urge the latter toward the normal position. Also a light spring 74 biases the rocker arm 68 toward cam-engaging positions.

Here again since the pivot shaft 69 is journaled on the frame 31, the movement of the transfer to the service position does not cause corresponding movement in the rocker arm 68 which remains in its normal position. Also the timing of the cams is arranged so that the cam 66 moves the lever 68 only when the first housing is in its lowered position. Therefore, the lifting of the pin 72 away from the projection 71 does not cause difficulty.

A separate cam driven linkage is provided to control the opening and closing of each pair of fingers 39. In the transfer mechanism illustrated in FIG. 3 there is provided three separate finger-operating linkages. However, in FIG. 6 only one such linkage is illustrated since it is representative of all of the fingeraoperating linkages.

Mounted on the camshaft 21 is a cam assembly 76 consisting of two separate cams which are individually adjustable with respect to the camshaft 21. With this arrangement one of the cams controls the opening of the fingers and the other cam controls the closing of the fingers. With this arrangement the cams can be separately adjusted to separately adjust the opening and closing of the fingers.

Pivotally mounted on the first support housing 32 is a rocker arm 77 provided with a roller follower 78 which engages the cam assembly 76. The forward end of the rocker arm 77 is provided with an operating surface 79 which is parallel to the pivot 81 of the rocker arm on the support housing 32. The operating surface 79 is also parallel to the line of motion of the transfer bar 38.

Each of the transfer fingers 39 includes a first finger assembly 82 and a second finger assembly 83. Two finger assemblies cooperate to provide a pair of opposed gripping fingers operable to grip a blank 84 and to transfer the blank from a first die 86 to a second die 87. The two finger assemblies 82 and 83 are separately pivoted on the transfer bar 38 with the finger assembly 82 carried by a pivot element 88. Mounted on the rearward end of the pivot element 88 is a follower arm 89 providing a roller follower 91 engageable with the operating surface 79.

Since the operating surface 79 is parallel to the line of motion of the transfer bar 38, the reciprocating movement of the transfer bar does not affect the position of the transfer fingers determined by the operating surface 79. Consequently when the low portions of the cam assembly 76 are under the cam follower 78, the spring 92 causes the fingers to close and grip a blank 84. Conversely when a lift portion of the cam assembly 76 passes the cam follower 78, the rocker arm 77 rotates in a clockwise direction and causes the finger assembly 82 to rotate in an anticlockwise direction as viewed in FIG. 6. This, through the connection at 93, produces clockwise rotation of the finger assembly 83 and results in opening of the transfer fingers.

The illustrated transfer is provided with three pairs of fingers 39, although only one pair is illustrated in the drawings. Referring to FIG. 3, a similar double cam 76a is provided to operate a corresponding follower arm 77a and a double cam 76b is provided to operate a follower arm 77b.

The mechanism for moving the transfer bar 38 includes a crank journaled on the machine frame and connected through a tie rod 97 to the transfer bar 38. The various elements should be arranged so that the transfer fingers are locatedin the gripping position when the arm 96 is in the position illustrated in FIG. 6 and after the arm has rotated through l80 the fingers are adjacent to the delivery position.

The operation of the mechanism can best be understood by referring to FIG. 6. The transfer fingers 39 are illustrated in full line at the gripping position. In this position the transfer fingersare located immediately in front of a die 86. Operation of the knockout mechanism (discussed in detail below) ejects the blank 84 from the die until it is supported entirely in the transfer fingers 39. During the first portion of the movement from the position 99 illustrated in full line, the operation of the cam 66 causes anticlockwise rotation of the second support housing 36 around the pivot 37 (See FIG. 4) to cause the fingers to move the blank along an arcuate path substantially perpendicular to the face of the die 86 to the first intermediate transfer position 101. The pivot 37 is substantially adjacent to the plane 105 of the face of the dies so that this motion is substantially perpendicular to the plane 105.

The crank 96 then causes the transfer bar 38 to move to the right to move the transfer fingers and the blank contained therein in a linear direction to a point 102 substantially in alignment with the die 87 The cam 66 then permits clockwise return movement of the second support housing 36 back to its initial position. This causes the transfer fingers to move inwardly toward the die 87 along an arcuate path substantially perpendicular to the face of the die 87. This movement carries the blank to a position at 103. A tool 104 carried by the slide of the machine then pushes the blank 84 from the fingers 39 into the die 87. The cam assembly 76 is arranged to open the fingers 39 as the tool 104 presses the blank into the die 87.

As soon as the blank is released from the transfer fingers the transfer can commence its return movement to its initial position at 99. This is possible in a machine incorporating the present invention because the cam 41 operates to lift the first support housing 32 so that the fingers are raisedclear of the tool 104 to permit such return movement before the tool completes its working operation and withdraws from the plane of transfer movement. It should be understood that theopening of the fingers combined with the raising of the fingers is arranged to provide this clearance. The pivot axis 34 is located a substantial distance back from the plane 105 so the pivotal movement raises the fingers and the path of return movement to the initial point 99 is a curved path as illustrated in FIG. 6. As soon as the transfer returns to its initial position at 99 and the blank is ejected a sufficient distance to clear the head in the case of a bolt blank, the fingers are allowed to'close by the cam assembly 76 to grip the blank and repeat the transfer operation. With this structure the dwell normally required at the delivery position is considerably reduced so the machine can be cycled at a higher cyclic speed without encountering transfer difficulties.

Referring to FIG. 7, the knockout mechanism includes the oscillating camshaft 23 on which is mounted a removable cam element 111 associated with each knockout mechanism. In the illustrated embodiment the cam element 111 is releasably clamped by a lock member 1 12 and a bolt fastener 113.

A knockout follower arm 114 is pivoted on the machine frame 10 for oscillating reciprocation about a pivot axis 116. An adjusting cam follower assembly 117 includes an adjustable block 118 on which is mounted a roller follower 119. An adjusting screw 121 adjustably positions the block with respect to the arm 114. This adjustment provides adjustment of the length of kick. Lock bolts 122 operate to lock the block in its adjusted position.

A compression spring 123 is connected between the frame 10 and the arm 114 to bias the arm 114 in an anticlockwise direction to maintain engagement between the follower 119 and the cam element 111.

The upper end of the arm 114 is provided with an adjustable threaded operator 128 which engages the rearward end of the knockout pin assembly 129. Reference may be made to the US. Letters Pat. to Maistros No. 3,171,144 for a detailed description of one knockout pin structure which may be used. The various elements are illustrated in the knockout position in which the blank 84 (illustrated in FIG. 6) is ejected from the die 86.

In accordance with the present invention the cam 111 is shaped so that the first portion of ejection occurs at a high rate so that the blank is moved out to position for gripping by the transfer fingers 39 in the shortest possible time. During this portion of a knockout operation, the cam element rotates so that the engagement between the follower 119 and thecam moves from the initial position on the cam at 131 to a position at about 132. When the blank is, for example, a bolt blank, the blank is then positioned so that the head of the blank is past the fingers and the fingers may close to grip the shank. During the gripping operation the ejection continues at a slower rate while the follower moves along the cam surface from the point 132 to the point 133. By the time the cam moves to a position in which the follower 119 engages the cam at the point 133 the gripping of the blank is completed and the ejection rate is then increased again to a higher rate as the cam follower rolls along the cam to the location at 134. This is the position illustrated in FIG. 7 in which the ejection is completed.

Because the ejection is arranged to first move at a higher velocity to move the blank to the blank gripping position, a minimum amount of time is required for this phase of operation. Similarly after gripping is accomplished the rate of ejection is again increased to minimize the time required for the completion of the ejection operation. This permits high-speed operation while providing reliable gripping of even short blanks.

Since the transfer incorporating this invention can operate with an active transfer cycle time which closely approaches the total machine cycle time, the machine can be operated with higher speeds without encountering transfer difficulties.

Further the in and out movement of the blankeliminates the need for precise adjustment of the knockout pin and also eliminates the requirement for spacing the subsequent dies back on the planes of the preceding dies.

Although a preferred embodiment of this invention is illustrated, it is to be understood that various modifications and rearrangements may be resorted to without departing from the scope of the invention disclosed.

We claim:

1. A forging machine or the like comprising a frame, a die breast having a lateral die face, a die in said die breast, a tool reciprocable in said frame toward and away from said die, gripper means supported on said frame adapted to grip articles at a gripping position and to transfer such articles to a delivery position adjacent said die, and power means operable to move said gripper means along a predetermined closed path, said closed path including a first portion of movement along a curved path about an axis substantially parallel to said die face at least the first part of which is substantially perpendicular to said die face from said gripping position, a subsequent second portion of lateral movement substantially perpendicular to said first portion of movement along a substantially straight path to a position substantially adjacent to said delivery position, a subsequent third portion of movement along an arcuate path substantially parallel to and in the opposite direction to said first portion at least the last part of which is substantially perpendicular to said die face to said delivery position, and a fourth portion of movement along a path back to said gripping position.

2. A forging machine as set forth in claim 1 wherein said pathof said fourth portion of movement is contained in a plane substantially parallel to a plane containing said path of said second portion of movement.

3. A forging machine as set forth in claim 2 wherein said path of said fourth portion of movement is curved.

4. A forging machine as set forth in claim 1 wherein said gripper means includes a pair of elongated gripper fingers adapted to grip a blank therebetween adjacent to one end of said fingers, and said path of said fourth portion of movement initially including lengthwise movement of said fingers in one direction and terminating in movement including lengthwise movement of said fingers in the opposite direction.

5. A forging machine comprising a frame, a die on said frame having a die face, a cooperating tool movable toward and away from said die, a pair of fingers on said frame operable to close for gripping a blank and operable to open to release a blank, first power means operable to move said fingers between a gripping position in which a blank is gripped and a delivery position in which a blank is positioned adjacent to said die, said tool operating to move a blank from said fingers into said die, said first power means operating to initiate return movement of said fingers from said delivery position toward said gripping position along a curved plane of movement while said tool continues to project through said curved plane, said fingers being opened and moved laterally clear of said tool along an arcuate path about an axis spaced back from the plane of said die face, and said axis being substantially parallel to said plane of said die face during said initiation of said return movement.

6. A forging machine as set forth in claim 5 wherein second power means are provided to move said fingers laterally clear of said tool during said initiation of said return movement.

7. A forging machine as set forth in claim 6 wherein third power means are provided to open and close said fingers.

8. A forging machine as set forth in claim 7 wherein fourth power means are operable to move said fingers away from the plane of the face of said die and substantially perpendicular thereto when said fingers commence to move from said gripping position to said delivery position, said fourth power means also operating to move said fingers substantially perpendicular to said plane of said die back towards said die as said fingers approach said delivery'position.

9. A forging machine as set forth in claim 8 wherein said power means are all driven in timed relation and said second, third, and fourth power means are all driven by a single camshaft. shaft.

10. A forging machine or the like comprising a frame, a die on said frame having a die face, a tool reciprocable toward and away from said die, a first housing pivotally supported said frame for oscillating rotation about a first axis substantially parallel to said die face, a second housing pivotally supported on said first housing for oscillating rotation about a second axis spaced from and substantially parallel to said first axis, a transfer bar reciprocably mounted on said second housing, gripper means mounted on said transfer bar operable to grip a blank at a gripping position and to transfer such blank to a delivery position adjacent to said die, and power means operable to oscillate said housings about said first and second axes and reciprocate said bar to move said grippers between said gripping and delivery positions.

11. A forging machine as set forth in claim 10 wherein said gripper means includes a pair of fingers operable to close to grip a blank and operable to open to release a blank, and said power means is connected to open and close said fingers.

12. A forging machine as set forth in claim 11 wherein said power means includes a camshaft journaled on said frame, and a separate cam driven linkage is operable to provide said oscillating rotation of said housings about said axes and operate said fingers.

13. A forging machine as set forth in claim 12 wherein said first housing is rotatable about said first axis to a service position in which the fingers are accessible for service and adjustment.

14. A forging machine as set forth in claim 13 wherein resilient means are supported on said frame, said resilient means being operable to urge said first housing toward a first position, and the associated cam driven linkage operating to oscillate said first housing against the action of said resilient means.

15. A forging machine as set forth in claim 14 wherein said resilient means is pivoted on said frame for pivotal movement about said first axis, and releasable locking means normally maintain said resilient means in an operative position, release of said locking means permitting movement of said first housing to said service position.

16. A forging machine as set forth in claim 10 wherein said first axis spaced back from and substantially parallel to said die face and said second axis located substantially in the plane of said die face.

17. A forging machine comprising a frame, a die on said frame, a cooperating tool on said frame reciprocable toward and away from said die, an ejector mechanism operable to eject the blanks from said die, and a transfer operable to grip and transfer blanks ejected from said die, said ejector mechanism operating to eject blanks at a first rate to a gripping position and to thereafter continue ejection at a second rate slower than said first rate, said transfer operating to grip a blank while it is being ejected at said second rate.

18. A forging machine as set forth in claim 17 wherein said ejector includes a cam drive proportioned to produced said first and second rates of ejection.

19. A forging machine as set forth in claim 17 wherein said ejector mechanism is operable after a blank is gripped by said transfer to eject such blank at a third rate which is faster than said second rate.

20. A forging machine as set forth in claim 17 wherein said transfer includes a pair of fingers on said frame operable to close for gripping a blank and operable to open to release a blank, first power means operable to move said fingers between a gripping position in which a blank is gripped and a delivery position in which a blank is positioned adjacent to said die, said tool operating to move a blank from said fingers into said die, said first power means operating to initiate return movement of said fingers from said delivery position toward said gripping position along a plane of movement while said tool continues to project through said plane, said fingers being opened and moved laterally clear of said tool during said initiation of said return movement.

21. A forging machine comprising a frame, a die on said frame having a face contained in a plane, a cooperating tool reciprocable in said frame toward and away from said plane, a first transfer frame pivoted on said frame for pivotal movement about an axis parallel to said plane on the side thereof opposite said tool, a transfer bar supported by said first transfer frame for reciprocating movement in a direction substantially parallel to said plane, first power means operable to cause oscillating rotation of said first transfer frame about said axis and second power means operable to produce said reciprocating movement of said transfer bar, and a pair of gripper fingers mounted on said transfer bar operable to grip a blank in a first position and to transfer such blank to a position adjacent to said die.

22. A forging machine comprising a frame, a die breast in said frame for supporting a plurality of dies at laterally spaced die stations each having a die face located substantially in a lateral plane, and a transfer assembly operable to progressively transfer workpieces laterally between said die stations, said transfer assembly including a power driven camshaft mounted on said frame for rotation about a first axis extending laterally with respect to said frame and substantially parallel to said plane, a first transfer housing, pivot means supporting said first transfer housing for oscillating rotation about a second axis substantially parallel to said first axis, a transfer slide mounted on said first transfer housing for lateral oscillating movement, a work gripper mounted on said transfer slide operable to grip a workpiece adjacent to one die station and carry it to a position adjacent to another die station, and a cam on said shaft operable to oscillate said first transfer housing and cause movement of said grippers toward and away from said die breast in timed relationship to the operation of said machine.

23. A forging machine as set forth in claim 22 wherein said transfer assembly includes a second transfer housing pivotally mounted on said machine for rotation about a third axis substantially parallel to said first and second axes, said pivot means being carried by said second transfer housing.

24. A forging machine as set forth in claim 23 wherein said second and third axes are on opposite sides of said first axis.

25. A forging machine as set forth in claim 24 wherein said second transfer housing is pivotable about said third axis from an operative position to a service position, movement of said second transfer housing to said service position moving said first transfer housing and said slide clear of said die breast and also providing improved access to said camshaft.

26. A forging machine as set forth in claim 22 wherein said gripper includes a pair of gripper fingers movable toward and away from each other to grip and release workpieces, and power means including a second cam on said camshaft are provided to operate and control the closing and opening of said fingers in timed relationship to the operation of said machine. 

1. A forging machine or the like comprising a frame, a die breast having a lateral die face, a die in said die breast, a tool reciprocable in said frame toward and away from said die, gripper means supported on said Frame adapted to grip articles at a gripping position and to transfer such articles to a delivery position adjacent said die, and power means operable to move said gripper means along a predetermined closed path, said closed path including a first portion of movement along a curved path about an axis substantially parallel to said die face at least the first part of which is substantially perpendicular to said die face from said gripping position, a subsequent second portion of lateral movement substantially perpendicular to said first portion of movement along a substantially straight path to a position substantially adjacent to said delivery position, a subsequent third portion of movement along an arcuate path substantially parallel to and in the opposite direction to said first portion at least the last part of which is substantially perpendicular to said die face to said delivery position, and a fourth portion of movement along a path back to said gripping position.
 2. A forging machine as set forth in claim 1 wherein said path of said fourth portion of movement is contained in a plane substantially parallel to a plane containing said path of said second portion of movement.
 3. A forging machine as set forth in claim 2 wherein said path of said fourth portion of movement is curved.
 4. A forging machine as set forth in claim 1 wherein said gripper means includes a pair of elongated gripper fingers adapted to grip a blank therebetween adjacent to one end of said fingers, and said path of said fourth portion of movement initially including lengthwise movement of said fingers in one direction and terminating in movement including lengthwise movement of said fingers in the opposite direction.
 5. A forging machine comprising a frame, a die on said frame having a die face, a cooperating tool movable toward and away from said die, a pair of fingers on said frame operable to close for gripping a blank and operable to open to release a blank, first power means operable to move said fingers between a gripping position in which a blank is gripped and a delivery position in which a blank is positioned adjacent to said die, said tool operating to move a blank from said fingers into said die, said first power means operating to initiate return movement of said fingers from said delivery position toward said gripping position along a curved plane of movement while said tool continues to project through said curved plane, said fingers being opened and moved laterally clear of said tool along an arcuate path about an axis spaced back from the plane of said die face, and said axis being substantially parallel to said plane of said die face during said initiation of said return movement.
 6. A forging machine as set forth in claim 5 wherein second power means are provided to move said fingers laterally clear of said tool during said initiation of said return movement.
 7. A forging machine as set forth in claim 6 wherein third power means are provided to open and close said fingers.
 8. A forging machine as set forth in claim 7 wherein fourth power means are operable to move said fingers away from the plane of the face of said die and substantially perpendicular thereto when said fingers commence to move from said gripping position to said delivery position, said fourth power means also operating to move said fingers substantially perpendicular to said plane of said die back towards said die as said fingers approach said delivery position.
 9. A forging machine as set forth in claim 8 wherein said power means are all driven in timed relation and said second, third, and fourth power means are all driven by a single camshaft. shaft.
 10. A forging machine or the like comprising a frame, a die on said frame having a die face, a tool reciprocable toward and away from said die, a first housing pivotally supported said frame for oscillating rotation about a first axis substantially parallel to said die face, a second housing pivotally supported on said first hOusing for oscillating rotation about a second axis spaced from and substantially parallel to said first axis, a transfer bar reciprocably mounted on said second housing, gripper means mounted on said transfer bar operable to grip a blank at a gripping position and to transfer such blank to a delivery position adjacent to said die, and power means operable to oscillate said housings about said first and second axes and reciprocate said bar to move said grippers between said gripping and delivery positions.
 11. A forging machine as set forth in claim 10 wherein said gripper means includes a pair of fingers operable to close to grip a blank and operable to open to release a blank, and said power means is connected to open and close said fingers.
 12. A forging machine as set forth in claim 11 wherein said power means includes a camshaft journaled on said frame, and a separate cam driven linkage is operable to provide said oscillating rotation of said housings about said axes and operate said fingers.
 13. A forging machine as set forth in claim 12 wherein said first housing is rotatable about said first axis to a service position in which the fingers are accessible for service and adjustment.
 14. A forging machine as set forth in claim 13 wherein resilient means are supported on said frame, said resilient means being operable to urge said first housing toward a first position, and the associated cam driven linkage operating to oscillate said first housing against the action of said resilient means.
 15. A forging machine as set forth in claim 14 wherein said resilient means is pivoted on said frame for pivotal movement about said first axis, and releasable locking means normally maintain said resilient means in an operative position, release of said locking means permitting movement of said first housing to said service position.
 16. A forging machine as set forth in claim 10 wherein said first axis spaced back from and substantially parallel to said die face and said second axis located substantially in the plane of said die face.
 17. A forging machine comprising a frame, a die on said frame, a cooperating tool on said frame reciprocable toward and away from said die, an ejector mechanism operable to eject the blanks from said die, and a transfer operable to grip and transfer blanks ejected from said die, said ejector mechanism operating to eject blanks at a first rate to a gripping position and to thereafter continue ejection at a second rate slower than said first rate, said transfer operating to grip a blank while it is being ejected at said second rate.
 18. A forging machine as set forth in claim 17 wherein said ejector includes a cam drive proportioned to produced said first and second rates of ejection.
 19. A forging machine as set forth in claim 17 wherein said ejector mechanism is operable after a blank is gripped by said transfer to eject such blank at a third rate which is faster than said second rate.
 20. A forging machine as set forth in claim 17 wherein said transfer includes a pair of fingers on said frame operable to close for gripping a blank and operable to open to release a blank, first power means operable to move said fingers between a gripping position in which a blank is gripped and a delivery position in which a blank is positioned adjacent to said die, said tool operating to move a blank from said fingers into said die, said first power means operating to initiate return movement of said fingers from said delivery position toward said gripping position along a plane of movement while said tool continues to project through said plane, said fingers being opened and moved laterally clear of said tool during said initiation of said return movement.
 21. A forging machine comprising a frame, a die on said frame having a face contained in a plane, a cooperating tool reciprocable in said frame toward and away from said plane, a first transfer frame pivoted on said frame for pivotal movement about an axis parallel to Said plane on the side thereof opposite said tool, a transfer bar supported by said first transfer frame for reciprocating movement in a direction substantially parallel to said plane, first power means operable to cause oscillating rotation of said first transfer frame about said axis and second power means operable to produce said reciprocating movement of said transfer bar, and a pair of gripper fingers mounted on said transfer bar operable to grip a blank in a first position and to transfer such blank to a position adjacent to said die.
 22. A forging machine comprising a frame, a die breast in said frame for supporting a plurality of dies at laterally spaced die stations each having a die face located substantially in a lateral plane, and a transfer assembly operable to progressively transfer workpieces laterally between said die stations, said transfer assembly including a power driven camshaft mounted on said frame for rotation about a first axis extending laterally with respect to said frame and substantially parallel to said plane, a first transfer housing, pivot means supporting said first transfer housing for oscillating rotation about a second axis substantially parallel to said first axis, a transfer slide mounted on said first transfer housing for lateral oscillating movement, a work gripper mounted on said transfer slide operable to grip a workpiece adjacent to one die station and carry it to a position adjacent to another die station, and a cam on said shaft operable to oscillate said first transfer housing and cause movement of said grippers toward and away from said die breast in timed relationship to the operation of said machine.
 23. A forging machine as set forth in claim 22 wherein said transfer assembly includes a second transfer housing pivotally mounted on said machine for rotation about a third axis substantially parallel to said first and second axes, said pivot means being carried by said second transfer housing.
 24. A forging machine as set forth in claim 23 wherein said second and third axes are on opposite sides of said first axis.
 25. A forging machine as set forth in claim 24 wherein said second transfer housing is pivotable about said third axis from an operative position to a service position, movement of said second transfer housing to said service position moving said first transfer housing and said slide clear of said die breast and also providing improved access to said camshaft.
 26. A forging machine as set forth in claim 22 wherein said gripper includes a pair of gripper fingers movable toward and away from each other to grip and release workpieces, and power means including a second cam on said camshaft are provided to operate and control the closing and opening of said fingers in timed relationship to the operation of said machine. 